CN1576129A - Three-piece motion control truck system - Google Patents

Abstract

An improved three-piece truck system for railroad cars provides long travel side bearings for improved stability, a 'wide' friction shoe design or equivalent to improve sideframe and bolster squareness, a resilient pedestal pad for improved curving performance and enhanced wear resistance, and a suspension system tuned and optimized for rail cars to have a minimum reserve capacity of less than 1.5 to improve motion control and ride quality, increase resistance to suspension bottoming, and increase hunting threshold speed. Such a motion control truck system is able to meet recent, more stringent American Association of Railroads standards, such as M-976, for railcars having a 286,000 lb. gross rail load rating.

Description

Three-piece motion control bogie truck system

Technical field

The present invention relates to a kind of improved three-piece bogie truck system that is used for the rail locomotive, this system provides the constant contact side bearing of long travel that is used to improve stability, friction shoe with squareness of improvement, one is used to the elastic support pad that improves curve performance and increase wear resistance, and has improved riding quality, has increased the sagging resistance of suspension, strengthened the suspension system that is used to adjust and optimize railcar of vibration terminal speed.Described motion control bogie truck system is believed to meet or surpass the M-976 code requirement of American Association of Railway (AAR).

Background technology

The two ends that railcar is relative are supported on the bogie truck assembly that is spaced apart out usually, and this allows described bogie truck to move along rail.The railcar of a standard comprises a pair of railcar bogie truck, this bogie truck comprises a pair of bogie side frame that is supported on the pair of axle spindles, each wheel shaft provides a pair of wheel, and wheel is firmly on each wheel shaft and separated from one another with the distance of the railway bogie specification that meets associating.Bogie side frame can vertically operate and be parallel to the longitudinal axis operation of described railcar along described bogie truck.Bogie side frame comprises a top member, a compression element, a take up member, a post, a gib, a bearing and a bearing top.

A hollow sleeper beam is arranged on the described longitudinal axis of described railcar sidewards, is connected with described bogie side frame, and has support railcar main body thereon.A sleeper beam center concave volume provides a central opening.One of the draw beam that concave volume reception of described sleeper beam center and support and car body are linked together protrudes the circular central dish.Described bogie pivot center concave volume provides main bearing surface to be supported on the described car body on the described bogie truck sleeper beam.The bogie pivot center concave volume is often suitable with a vertical wear ring with a horizontal scuff panel, to improve wearing character and to prolong service life of described associating bogie truck sleeper beam.

Each bogie side frame comprises a window portion of the spring assembly that is used for the sleeper beam end and has been used to support described sleeper beam, and this window portion allows sleeper beam to move with respect to described bogie side frame.Each spring assembly typically comprises a plurality of wind springs, and wind spring extends between a lower surface of the described sleeper beam of a bogie side frame spring perch partial sum end, and described sleeper beam end is spaced apart above bogie side frame spring perch separately.

Side bearing also can be arranged between described bogie truck sleeper beam and car body, typically is provided to from the side on each limit of spider concave volume, and the spider concave volume on the sleeper beam is on described bearing gasket.Constant contact side bearing uses on the railcar bogie truck usually.They typically are arranged on the described bogie truck sleeper beam, such as on the side shaft rim, but can be set at other places.An independent coil spring that is installed between base and the lid has been used in design before some.A plurality of coil springs or elastic element have been used in other design.

The transport truck bogie truck amount of capacity of American Association of Railway (AAR) standard is generally demarcated by the nominal load-bearing capacity or the specified load-bearing capacity of the railcar of having equipped such bogie truck.Representative type bogie truck capacity performance index is 40 tons, 50 tons, 70 tons, 100 tons and 125 tons.The more specifically index of bogie truck capacity is the permission total gross weight that is equipped with on the rail of railcar of special capacity bogie truck.The example of such a bogie truck capacity performance index is respectively 142,000 pounds, 177,000 pounds, 220,000 pounds, 263,000 pounds and 315,000 pounds.Since 1994, AAR standard transport truck bogie truck is at the commercial railcar that can be used to have 286,000 pounds of rank gross weights.

The total permission gross weight that is used for the railcar bogie truck on the rail or maximum gross weight normally by journal bearing on the railcar bogie truck wheel shaft of associating load-carrying capacity determined.And, with each nominal railcar bogie truck capacity linked together be given wheel diameter size, in order to the restriction maximum wheel/rail contact pressure.The representative type journal bearing size and the wheel diameters that meet AAR standard transport trolley bogie truck are included in the following form.

Table 1

Maximum gross weight journal bearing size wheel diameters diameter on the nominal bogie truck capacity rail

40 tons 142,000 pounds 5 inches * 9 inches 33 inches

50 tons 177,000 pounds 5.5 inches * 10 inches 33 inches

70 tons 220,000 pounds 6 inches * 11 inches 33 inches

100 tons 263,000 pounds 6.5 inches * 12 inches 36 inches

125 tons 315,000 pounds 7 inches * 12 inches 38 inches

American Association of Railway (AAR) is that railcar stability, wheel weight and spring assembly structure have been set up standard.These establishments of standard or determine to make in this case, promptly, admit that the dynamic mode of vibration of railroad car body as the waving of enough amplitudes can compress the individual spring of the described spring assembly of the end, interval that is positioned at described sleeper beam, compression of spring even arrived entity state or near entity state.The length of spring compressed of this end, interval is accompanied by the stretching, extension of spring, " surface " wheel weight and the railcar oscillating motion subsequently on described suspension system can be amplified and enlarge to this effect-counteraction, just as with opposite from described railcar and wherein actual or " on average " weight or load.As the result of the oscillating motion of amplifying, and when the large amplitude of such oscillating motion, the contact-point pressure between described rail and the described wheel can significantly reduce at the interval of described railcar side.In an extreme example, described wheel can promote also from described bogie truck and depart from it, and this has increased the chance of overstepping the limit.

Railroad car body motion has multiple mode, upsprings, jolts, deflection and swaying and swing above-mentioned.At vehicle body swing, perhaps in the distortion and swing by AAR definition, described car body looks like alternately near rotation between the side of described railcar and the longitudinal axis.Car body jolts and can be regarded as the motion that near the past horizontal railcar rotation axis rotates backward, states railcar like this and may look like at it and advance by leaps and bounds forward and between the longitudinal direction backward.The upspring motion of the vertical and straight line that refers to described railcar of car body.Deflection is considered to be at passes near the rotatablely moving vertical axis that described railcar extends, and this has provided along with described railcar moves on to the presentation that lower, described compartment end move back and forth with bogie truck.At last, lateral stability is counted as the vibration horizontal transfer of described car body.As selection, bogie truck vibration refers to described railcar bogie truck, rather than the parallelogram degree or the degree of deformation of described railroad car body, and this is distinct phenomenon of separating with the motion of described railroad car body above-mentioned.The bogie truck vibration also is because the wheel cross-sectional plane is conical thereby the vibration horizontal transfer of the described spoke of generation.All these mode of motion do not wish to take place, and can cause unacceptable railcar performance, and are unfavorable for the safe in operation of railcar.

A device commonly used that is used for controlling the dynamic response of railcar bogie truck and railroad car body is the friction shoe assembly, and it provides the damping from the sleeper beam to the bogie side frame of vibratory movement.Friction shoe is included in a drag wedge in the sleeper beam depression, is biased to keep and described bogie side frame friction engagement at wedge described in this sleeper beam depression.Thereby friction shoe has consumed the suspension system energy by frictional damping is carried out in the relative motion between described sleeper beam and the bogie side frame.

Friction shoe the most normally is to use the frictional damping structure of constant or droop, and described friction shoe contacts the inside face of supplying of described sleeper beam depression simultaneously.Make described friction shoe that deviation be arranged and of keeping this friction shoe to be resisted against on described sleeper beam depression surface and the described bogie side frame post rubbed surface keeps spring or controlling spring partly to be supported by the spring substrate or the spring pedestal of the described bogie side frame of described friction shoe below.By a fixing or constant deviation or damping spring group, described controlling spring does not carry, and described friction shoe assembly compression of spring rate is remaining unchanged during the relative motion between described sleeper beam and the bogie side frame basically, and this bulk compressibility is the displacement as a function of power.Therefore, in a constant bias is arranged, all situations for described railcar load, the bias force that acts on described friction shoe keeps constant in the whole operation scope, this opereating specification not only is used for described relative motion, and is used for the spring displacement of the biasing between described sleeper beam and the bogie side frame.Therefore, described friction shoe is relative constant with the friction force maintenance between the post worn-out surface.

As selection, the reaction of the friction shoe in variable deviation is arranged changes along with described maintenance compression of spring length.Therefore, the friction force between described friction shoe and the described bogie side frame post changes along with the perpendicular movement of described sleeper beam.Yet, in the variable structure of spring rate, the opereating specification of described controlling spring or spring rate may be not sufficient to applied force is made a response, and these power are the weight of described railcar and the dynamic force of vibration just, and dynamic force is the change from described bogie truck and operating conditions.At least in some variable friction force are arranged, distance between described friction shoe and the described bogie side frame spring perch has been considered to be enough to provide suitable design characteristics to the friction shoe bias spring, handling the variation and the scope of power in described railcar wheel bogie truck assembly, even can be used to have the railcar of a higher nominal load-carrying capacity.

In fixing or constant deviation were arranged, described friction shoe often had a spring depression and receives a controlling spring with sufficient length and wind spring diameter, in order to needed frictional damping to be provided.

Described spring assembly is arranged and is supported described railcar together with described friction shoe, and mutual action relative between described sleeper beam and the bogie side frame is suppressed.The spring assembly that has had a plurality of types that are used for the railcar suspension system is such as at described spring assembly in-to-in concentric spring; Five, seven and nine springs are arranged; The elongation spring that is used for described friction shoe; And be used for short elastic length spring at the described friction shoe of the secondary in-to-ins of many springs.These only are arranged on several in arranging of a lot of famous spring between bogie side frame and the sleeper beam end assembly.These spring assemblies must meet the standard that American Association of Railway (AAR) is formulated, this standard code under compressive state or entity spring state fully the fixing spring height of each wind spring.The special spring rows row that are used for any railcar depend on the physical structure of described railcar, the structure of its specified load-carrying capacity and wheel steering frame component.That is to say, described spring assembly is arranged and must be made a response to the variation in the described bogie truck, and the variation in the described railcar made a response, such as the available vertical space between the railcar weight of sky, fully loaded railcar weight, railcar distribution of weight, railcar character of operation, described bogie side frame spring platform and the described sleeper beam end, special friction shoe design and other operation and parameter physics.

Spring assembly design consideration AAR standard S-259 in the past and rule 88 are limited on 1.5 the minimum reserve power.Although the reserve power minimum value of this permission is 1.5 according to the AAR standard, the suspension reserve power that is used for the frictional damping body suspension reduces for the hauling engine of railcar, because they are equipped with the suspension system of oneself.Reduce reserve power for the load of these types and be believed to improve riding quality.Except the railcar hauling engine, the minimum reserve power of AAR1.5 is considered to prevent that the sagging minimum of suspension from allowing the spring ability.Yet former technology is not considered the length of described railcar or at the mutual action of the described suspension system of car in-to-in.All types of cars all use same suspension design and damping.

Described railcar must can bear rated load, nominal load weight physically, and along with railcar keeps contacting with described track with the speed operation that changes along different track profiles, and different track profiles has the track condition of variation.Simultaneously, described railcar and bogie truck assembly must have make oneself can be under these the same track conditions that change under unloaded, the empty wagons situation character of operation of safe in operation.Two of Operating Weight extremely all must be conditioned not causing under the urgent situation of overstepping the limit under arbitrary situation.

For top required opereating specification ability is provided to railcar, the described damping system spring assembly that is combined into one with described bogie truck assembly must have definite static state and dynamic operating characteristic.That is to say that operate the dynamic operation problem that can cause coming self-excited oscillation to changing the car that moves on the very wide rail in track and profile condition, this can develop into the uncontrolled fugitiveness of described railcar, especially on the curve that extremely raises.Track is the result of several conditions with separating of wheel, comprises that rail is defective cross-section, and with because the oscillation frequency of the car that takes place by the disunity track cooperate, the wheel disengaging of unloaded railcar is not rare.Although wheel breaks away from from track and do not cause derailing usually, be easy to become obvious danger yet separate the implicit danger that causes like this, and if possible should avoid.

One of main method of the vibration of processing railcar and bogie truck assembly is the damping from friction shoe above-mentioned, also has the stability influence of described support spring.These vibrations may partly be because the physical track condition that railcar experienced in its operating period produces.Give an example, the change of track condition can influence the operation of described bogie truck assembly, thereby the influence that this track changes can be exaggerated along with they are transferred on the described bogie side frame by wheel, wheel shaft and suspension.This can be along with thereby railcar passes track and meets with the operation that operational issue that more these tracks cause influences railcar.

It is the vibration that is designed to control described railcar that the representative type side bearing is arranged.That is to say,, in described railcar bogie truck, caused the motion in a deflection axle center along with the half-conical wheel of described railcar bogie truck travels along rail.Because truck swing, the part of described side bearing be made into to slide cross described railroad car body below.Synthetic friction has produced an opposite moment of torsion, and this moment of torsion has produced the effect that prevents this yaw motion.Another purpose of railcar bogie truck is control or the oscillating motion that limits described car body.Side bearings design before the great majority with the stroke limitation of described bearing about 5/16 ".The range of such a side bearing is by American Association of Railway (AAR) prescribed by standard.Standard in the past, such as M-948-77, with the stroke limitation much used 5/16 ".

New standard develops, and this needs the railcar bogie truck to meet exacting requirements more.Up-to-date AAR standard is M-976, and this standard is applicable to the railcar with the total orbital payload that surpasses 268,000 pounds.

Summary of the invention

Existence is to the needs of the improved bogie truck that is used for railcar, and this bogie truck meets these new AAR standards, such as the M-976 or the rule 88 of AAR official manual regulation.

Also have the needs to a kind of improved railcar bogie truck, this railcar bogie truck has the cooperative project organization of a cover, and is in order to motion control and the character of operation that improvement is provided, especially favourable in the time of the transportation big capacity load.

Above and other advantage be that variation by embodiments of the invention obtains.

In a preferred embodiment, improved motion control bogie truck has merged two or more in the following structure: the constant contact side bearing of long travel; Have increase squareness " wide " friction shoe structure or similarly replace structure with it, such as the split wedge friction shoe, perhaps compound oblique angle watt; Elastic support pad and/or an elastic support pad; And a suspension system, suspension system is lower than 1.5 reserve power by " adjustment " and optimization to have.In a most preferred embodiment, all these four project organizations are integrated in the motion control bogie truck, and be considered to have compound effect, described bogie truck is met or surpass the AAR standard, M-976 such as the railcar that is used to have 286,000 pounds of total value orbit determination road loads.

The long travel side bearing can obtain by arbitrarily different designs traditional or development subsequently, and in these designs, the stroke of described side bearing allows to surpass 5/16 ", preferably at least 5/8 ".Give an example, this can realize by using an elasticity propulsion element, such as an elastic element or be arranged at base and lid between one or more springs.In an exemplary embodiment, long travel can be arranged at a side bearing that is used for the railcar bogie truck and realize, this be by several structures in conjunction with realizing, comprise reducing and/or the reducing of described elasticity propulsion element entity height of base and/or lid height, to be held at least 5/8 before and before described base and lid reduce as far as possible by compression (entity) fully at described propulsion element " stroke.

In an exemplary embodiment, the improvement operation that comprises the described side bearing of the control of improvement and vibration characteristic realizes by the axial clearance between the described lid and bottom seat of careful control.Have been found that this for prevent between the described lid and bottom seat excessive mobile be very important, and reduced shock pressure, stress and the wearing and tearing of associating.

In an exemplary embodiment, the track, curve and the load horizontal properties that improve under the situation that does not have the reverse influence oscillating characteristic, have been obtained, thereby this is to change within the preset range by the spring constant with described side bearing to realize that this scope is preferably between 4000-6000 pound/inch.

In an exemplary embodiment, it is that the planeness of the corner of the lid by handling described side bearing and the last mating surfaces that increases described lid is to improve wearing character that better mating surfaces with a car body scuff panel is arranged, abrade such as reducing, thereby obtain.

In an exemplary embodiment, the squareness of improvement is by using a wide friction shoe design to obtain.In a specific embodiments, with representative type 51/2 " wide friction shoe compares, described friction shoe width approximately is 8 " or wideer.

In an exemplary embodiment, thus the squareness of improvement also can have compound oblique angle to increase a watt of acquisition of squareness by using the design of split wedge friction shoe or using.

In an exemplary embodiment, thus the curve of improvement obtains by using elastic support pad.

In an exemplary embodiment, described bogie truck is shaped to allow the higher effective load-carrying capacity by light casting.

In an exemplary embodiment, the riding quality of improvement, the vibration terminal speed of sagging resistance of suspension and increase is adjusted suspension and obtained by improving, this is adjusted suspension and has nest spring, and this nest spring has and is lower than 1.5 minimum reserve power.Give an example, this can obtain by total quantity or the alternative employed types of springs that reduces spring.

Description of drawings

The present invention will describe with reference to following accompanying drawing, wherein:

Fig. 1 is the oblique drawing of railcar wheel bogie truck assembly;

Fig. 2 is the semi-sictional view exploded drawings at bogie side frame, spring assembly, sleeper beam end and the friction shoe of described wheel steering frame component one side of Fig. 1;

Fig. 3 is the oblique drawing of the wheel steering frame component part of assembling shown in Figure 2;

Fig. 4 is the planar view of a sleeper beam end and friction shoe depression thereof;

Fig. 5 is the front elevation of the part of described spring assembly, sleeper beam end and friction shoe;

Fig. 6 is the declivity upward view that wing friction shoe is arranged;

Fig. 7 A is an oblique drawing as the embodiment that selects of friction shoe;

Fig. 7 B is an oblique drawing as the embodiment that selects of friction shoe;

Fig. 7 C is an oblique drawing as the embodiment that selects of friction shoe;

Fig. 7 D is an exploded drawings as the embodiment that selects of friction shoe;

Fig. 7 E is the oblique drawing of friction shoe shown in Fig. 7 D;

Fig. 8 A is the front elevation of the constant damping axle spring group in the bogie side frame with a friction shoe;

Fig. 8 B is the front elevation of the adaptive damping axle spring group in the bogie side frame with a friction shoe;

Fig. 9 is the front elevation of the spring assembly in the bogie side frame with a friction shoe;

Figure 10 A is an exemplary spring in free height;

Figure 10 B is the spring that is compressed to Figure 10 A of complete vehicle curb condition height;

Figure 10 C is the spring that is compressed to Figure 10 A of fully laden height;

Figure 11 is the planar view of standard nine nest spring's structures; And

Figure 12 is the planar view of nine nest spring's structures of a preferred embodiment;

Figure 13 is the chart of normal acceleration, has showed a function as described railcar speed;

Figure 14 is the planar view of standard seven nest spring's structures;

Figure 15 is the planar view of seven nest spring's structures of a preferred embodiment;

Figure 16 is to fall and a diagram of the variation of upspringing in the bogie truck surface;

Figure 17 is the decomposition diagram according to exemplary constant contact side bearing of the present invention;

Figure 18 is the top view according to exemplary side bearing base of the present invention;

Figure 19 is the cutaway view of the described base of Figure 18 along line 19-19;

Figure 20 is the top view according to exemplary side bearing lid of the present invention;

Figure 21 is the cutaway view of the described lid of Figure 20 along line 21-21;

Figure 22 is the cutaway view of the described lid of Figure 20 along line 22-22, and its structure is to be used to receive one or more springs;

Figure 23 is a form that is used for exemplary side bearing spring assembly of the present invention;

Figure 24 is the cutaway view of the described side bearing lid of Figure 20 along line 22-22, has showed the first exemplary rim lock locking structure;

Figure 25 is the cutaway view of the described side bearing lid of Figure 20 along line 22-22, has showed the second exemplary rim lock locking structure; And

Figure 26 is the cutaway view of the described side bearing lid of Figure 20 along line 22-22, has showed the 3rd exemplary rim lock locking structure, is used for an independent big spring.

The specific embodiment

As shown in Figure 1, an exemplary railcar wheel bogie truck assembly 10 has one first bogie side frame 12 and one second bogie side frame 14, and they are arranged parallel to each other.Horizontal sleeper beam 16 links together them at first bogie side frame 12 and second bogie side frame 14 spring window 18 places separately usually, and the spring window is roughly in vertical midpoint of first and second bogie side frames 12,14.First wheel shaft and wheel set 20 and second wheel shaft and wheel set 22 are arranged on the opposite end of parallel bogie side frame 12 and 14.Each of first and second wheel shaft and wheel set 20,22 all has an axle axis 30, and this axle axis is usually transverse to the longitudinal axis 31 of first and second bogie side frames 12,14, and is roughly parallel to sleeper beam 16.Each of first and second wheel sets 20,22 all comprises wheel 24 and 26 and wheel shaft 28 with axle axis 30.

Sleeper beam 16 has first end 32 and second end 34, and they extend respectively by the window 18 of first and second bogie side frames 12,14 of Fig. 1.First friction shoe 38 of window 18, sleeper beam end 32, spring assembly 36, bogie side frame 12 and second friction shoe 40 are demonstrated with view that amplify, that analyse and observe, that decompose in Fig. 2.Because sleeper beam end 32 and 34, first and second bogie side frames 12 and 14, and bogie side frame window 18 is all similar on 26S Proteasome Structure and Function, so only the sleeper beam end 32 on first bogie side frame 12 will be described, but this describes sleeper beam end 34 and the window 18 that also is suitable for second bogie side frame 14.

In Fig. 2, bogie side frame window 18 has lower support platform 42, and this platform has first and second vertical lateral column or side 44 and 46, and they are respectively from platform 42 vertical extent.Spring assembly 36 is depicted as three or three matrixes of being made up of loading spring 48,54 and 56.In this matrix, the first inner control spring 50 and second controlling spring 52 are arranged in the outer control spring 54 and 56 with one heart, and they provide the controlling spring assembly respectively, and these controlling springs 50,52,54 and 56 also are the load-carrying units of railcar.Bearing spring 48, perhaps the bearing spring assembly can comprise 1,2 or 3 individual springs, they are in the mode that satisfies design standard or can be that suspension spring group 36 provides the mode of the tractive performance of optimization to arrange.

Thereby described spring assembly 36 can reach adjustment by the quantity that changes spring, the arrangement of spring and/or the type of spring.Therefore, picture is in this uses, the definition of term " adjustment spring assembly " means from the amended spring assembly of a standard spring assembly design (have the actv. of the present invention the time typically require reserve power greater than 1.5 according to AAR (American Association of Railway)), this modification is by removing, replace, and/or rearrange that the not standard group spring of additional any other device of certain type realizes, give an example, for example liquid-damped interpolation, this liquid damping is in place in described spring assembly component internal, and this coordination has reduced the reserve power of described spring assembly described here according to expection.The removing of spring comprises and removes in the sleeve spring one or more, perhaps removes a sleeve spring in described spring assembly inside.Particular type spring alternative comprises and substitutes in the sleeve spring one or more, perhaps substitute an original sleeve spring with a different spring or different sleeve springs in described spring assembly inside, give an example, substitute with a spring of different hardness, size or similarity.Adjusting the example of spring assembly assembly is further discussed below.

Sleeper beam end 32 among Fig. 2 and Fig. 4 is friction shoe depression 61 before sleeper beam front edge 58 places have, and has back friction shoe depression 63 at sleeper beam lagging dege 60 places, friction shoe depression 61 and 63 receives first and second friction shoes 38 and 40, and they are slide therein separately.The bogie side frame 12 of Fig. 2, sleeper beam 16 and spring assembly 36 are showed in Fig. 3 with the form of assembling.In this drawing, notice that the inside face contact is arranged between the friction face 62 of lateral column rubbed surface 46 (Fig. 2) and friction shoe 40.Similarly friction face 62 also is suggested in other friction shoe of friction shoe 38 and wheel bogie.Just between a friction shoe and rubbed surface, for example between friction shoe 40 and the rubbed surface 46, the friction inner surface movement dumping force of friction shoe just is provided.Provide the eccentric force that acts on the friction shoe 38,40 by controlling spring 50,52,54,56, this eccentric force acts on friction shoe lower surface 64 places as shown in Figure 5.

When sharing load with described loading spring 48, friction shoe 38,40 is just operated as damping arrangement.Friction shoe 40 among Fig. 6 is one wing friction shoe, and it has core 41, first wing 43 and second wing 45.Friction shoe core 41 can be slidably moves in the groove 61 or 63 of sleeper beam end 32, and as shown in Figure 4, this is in order to keep friction shoe 40 in position, and in the friction shoe up-and-down movement process of railcar during through rail to its channeling conduct.Yet, controlling spring, the described off-centre of spring assembly or couplet 50,54 and 52,56 operates on the friction shoe 38,40 of uniting with them variable eccentric motion is provided, and this has regulated the power operation scope of wheel steering frame component 10 and wheel bogie (not shown).In Fig. 6, the annular disk or the endless belt thing 47 that are arranged on lower surface 64 centers usually extend into control wind spring 52 from lower surface 64, so that spring 52 is kept in-line.Spring 52 contacts with following watt of surface 64, and bias voltage friction shoe 40, is used for providing damping to sleeper beam 12 and bogie truck 10, and therefore provides damping for described railcar.

In the common operation of a railcar, spring assembly 36 bias voltage sleeper beams 16, and therefore described railcar is supported at spider 66 places by sleeper beam 16.Described eccentric force control or regulate the vibration or the jump of described railcar through keeping the stable of railcar in the described rail process, and carries out damping to any disturbance from various uncertain influences, mentions just as top.

In the former typical structure, friction shoe has about 5.5 " the cross-section friction face 62 of width.Yet, in one exemplary embodiment of the present invention, the friction shoe that has been found that a broad helps improving squareness, and help in the different bogie truck part cooperation of adjusting spring assembly 36, running well with other, in order to obtain a bogie truck design, this design can be satisfied the standard of nearest AAR for the big railcar as M-976.Especially, have been found that to have one about 8 " wide or even " wide " friction shoe of wideer friction face 62 rectangle that improves is provided.The increase of described friction shoe width has reduced the amplitude that bogie side frame 12,14 " waves " with respect to sleeper beam 16 described near curve the transportation.This makes described bogie truck at all keep if having time rectangle (that is to say described bogie side frame hang down in fact as for described sleeper beam) and helping described bogie truck to recover " rectangle " later on by a turning.This has reduced the wearing and tearing on described bogie truck, wheel and rail.

In Fig. 7 A-7E, 8A and 8B, expressed and be used for described friction shoe and be used to have the structure that the conduct of the described friction shoe of spring assembly is selected.Should be noted that different friction shoe designs can be used in railway bogie suspension design of the present invention.The main key of improving performance is that friction shoe uses in conjunction with other design feature, thereby improves the moving-mass of bogie truck by the squareness that increases described bogie truck.

Fig. 7 A illustrates a friction shoe 150 that does not have the double-vane structure.Fig. 7 B illustrates the friction shoe 150 with a liner 151.Fig. 7 C illustrates a friction shoe 152 as selection with a pair of liner 153.Another is the separating wedge structures with an embolus 155 as the friction shoe of selecting 154 in Fig. 7 D and figure E.As the friction shoe of selecting, embolus 155 combines with a sleeper beam depression by this.In transportation, when sleeper beam 16 moved down, the wedge element that constitutes two separation of friction shoe 154 outwards stretched.This has increased the Effective width of described friction shoe gradually along with the increase of transportation, thereby has increased the eccentric force that applies, and has caused the squareness of improving, and this squareness can be comparable to the squareness that obtains by the friction shoe design of fixing " width ".

In Fig. 8 A, represented second as the friction shoe of selecting 247 in the illustrative part of a constant damping axle spring group in a bogie side frame and sleeper beam.In this structure, friction shoe 247 has out the end opening 249 to the inner room 251 of friction shoe 247.Controlling spring 52 bias voltages in chamber 251 watts 247 make it near sleeper beam 36.In this structure, friction shoe 247 can have arbitrary shape, as double-vane or monocline face.In Fig. 8 B, the bogie side frame in another embodiment of the present invention and the illustrative adaptive damping axle spring group of sleeper beam represented described second as the friction shoe of selecting 247.

As shown in Figure 9, the typical wear of the element of wheel steering frame component (in Fig. 1 10) occurs in rubbed surface 46, friction face 62 and described friction shoe skewed surface 51.Such wearing and tearing cause described watt depression 63 inner raise of described friction shoe at described sleeper beam 16.Along with described friction shoe 40 raises, described control wind spring 57 decompressions cause column load 55 to reduce.Therefore, the measurement of described friction shoe height is that whole control element worn-downs are comprehensively measured.Described friction shoe has an appreciiable indicating device 49, in order to determine when described friction shoe should be replaced because of surface abrasion.

Described shock damping action by implementing as the device of friction shoe 38 and 40, all is manipulable at relative sleeper beam end 32,34 and at front edge and lagging dege 58,60 places often.Yet, not merely be an eccentric force to the applying of sleeper beam end 32,34 and friction shoe 38,40, also have applying of static load (pressure on described spring), be only described railcar or weight when unloading or full load.Yet for any specific railcar, the weight of described railcar is variable, this weight has the scope of broad, from an empty wagons, railway carriage weight extends to the railcar weight of a full load capacity, and may over proof vehicle load weight.Because described railcar orbits, so it has experienced the dynamic compression force on the spring, and it is subjected to all above-cited track condition influence easily, also is subject to countless other condition effect simultaneously, and these influences can cause vibration.Spring assembly 36 and friction shoe 38,40 concerted activities are to provide required damping to described railcar and wheel steering frame component 10, to be used for its safe in operation.

In Figure 10 A, exemplary spring 270 illustrates the free height X of spring and the entity height A of compression or machinery fully.In Figure 10 B, spring 270 has been compressed a compression distance y ', the spring height y when reaching static empty wagons, and in Figure 10 C, the full load capacity car has compressed a compression distance z ' with spring 270, reaches spring height z.In dynamic operation, described railcar will vibrate near static height, and it will compress and stretch described spring near these static height.Distance A in Figure 10 C ' be deposit distance or the safety distance that is designed in the spring, be used to regulate any ccasual vehicle vibration that has surmounted conventional expectation value.

On the structure between the transport capacity of railcar weight that reduces and increase and operational contradiction be a main operational scenario, this situation must be regulated.Complicated factors comprises the standards and norms that AAR formulates for the railcar that utilizes in exchange more, and this is at a lot of railcars rather than mono-user, so these standards and norms are subjected to the protection of AAR.Restricted weight factor has caused operational constraint to the designer.Although the user wishes the transport capacity maximization of railcar and minimize weight, yet the character of operation of safety all at first will be concerned about the supplier and the user of railcar.

What can indicate railcar suspension and damping structure is spring assembly 36.The ratio or the response of the spring of arranging for an independent concentric spring, and the quantity of the required spring arranged of the difference that needs in a specific spring assembly 36 all will change for a specific wheel steering frame component 10 and the type of railcar.By the quantity that changes spring, the arrangement of spring, and/or the type of spring, the riding quality and the vibration limit have significantly been improved.Give an example, nine disc spring groups 36 of a standard comprise nine outer spring 36A and eight inner spring 36B, as shown in figure 11.For 286,000 pounds of railcars that use these standard nine disc spring component Design and bogie truck assembly (not shown), described column load is 4,744 pounds, and the group ratio of described spring is 29,143 pounds of per inchs; Described dumping force is 2,134 pounds; And deposit is than being 1.61.Comparatively say, design for 9 outer helical spring 36A of use shown in Figure 12 and " adjustment " spring assembly of 6 interior disc spring 36B, described column load is 5,996 pounds, and the group ratio of described spring is 26,061 pounds of per inchs; Described dumping force is 2,698 pounds; And deposit is than being 1.47.The quality of described adjustment design consideration vehicle main body and the position of geometric configuration and bogie truck and increased damping and reduced the spring reserve power.Design suspension system in this mode and need reduce reserve power with to 1.5 dressing of being lower than the AAR standard.This is tested mistake the on a lot of cars, and shows on the riding quality and the vibration limit and be significantly improved.

With reference to Figure 13, a chart has been showed the normal acceleration speed of railcar, and this is illustrated as its velocity function.Near accelerating to 55mph, its dominant record normal acceleration is near 2.5 grams as 286,000 pounds of railcars with standard nine disc spring groups and bogie truck ' second.Relatively, as having 286,000 pounds of railcars of spring assembly design-calculated of adjustment and bogie truck near accelerating to 55mph, its dominant record normal acceleration is near 1.1 grams ' second.Reach and be lower than 1.5 by reducing reserve power, the maximum perpendicular acceleration/accel has reduced significantly, has improved the riding quality and the vibration limit.

This is adjusted design the riding quality that improves is provided, increased the resistance sagging to suspension, and strengthened the vibration terminal speed of railcar, and be to make bogie truck can meet the factor that works of new AAR bogie truck performance specification M-976 therefore, may be not enough although use described adjustment spring assembly separately for making bogie truck satisfy such new criteria.More suitably, may need the associating of several bogie truck parts, as descending the one or more of surface parts: the elastic support pad; The constant contact side bearing of long travel; " wide " friction shoe or other friction shoe with squareness of increase; And/or lightweight casting frame.Preferred embodiment comprises described adjustment spring assembly and long travel side bearing at least, but may further include the friction shoe design and/or the elastic support pad of improvement.Most preferred embodiment has used all these four bogie truck parts.

In another embodiment of the present invention, seven disc spring design components of a standard are adjusted to improve the riding quality and the vibration limit.Clearly, as shown in figure 14, standard seven disc spring groups 36 have 7 outer spring 36A, 9 inner spring 36B and 5 inner spring 36C.For 286,000 pounds of railcars, this design has 4,744 pounds column load, the spring assembly ratio of 30,562 pounds of per inchs; Be equivalent to 2,134 pounds dumping force and deposit than being 1.57.By remove described in-inner spring 36C and substitute described controlling spring, as shown in figure 15, for 286,000 pounds of railcars, described column load is increased to 5,996 pounds, described group of ratio drops to 25,781 pounds of per inchs; Described dumping force is increased to 2,698 pounds; And deposit is than dropping to 1.42.Again, one is lower than 1.5 deposit than the riding quality that has caused improving and the vibration limit.

Should be noted that a lot of different standard disc springs designs are using at large, such as give an example, these assemblies comprise 1) have 9 outer springs of 7 inner springs; 2) have in 7 inner springs, 2-7 outer springs of inner spring and two control wind springs; 3) have 7 outer springs of 7 inner springs and two controlling springs; 4) have in 7 inner springs, 2-7 outer springs of inner spring and bilateral disc spring; 5) have in 7 inner springs, 4-6 outer springs of inner spring and bilateral disc spring.Each can as discussed abovely be adjusted these standard disc spring design-calculateds like that to have and be lower than 1.5 reserve power.

Notice that described adjustment design is that to be used for an interactional example of the particular length of car and described car inner suspension system be very important.The spring assembly that is used for different vehicle types is adjusted the performance of optimizing to obtain, and this can cause being lower than 1.5 deposit ratio.Reduce to by spring assembly reserve power and to be lower than 1.5, just obtained to reduce the beyond thought result of maximum perpendicular acceleration/accel the railcar of given weight and structure and bogie truck.The vertical minimizing of quickening has allowed the improvement of riding quality, has increased the sagging resistance of suspension and has increased the vibration terminal speed of described railcar.

As described above, the reserve power of spring assembly adjusted to be lower than 1.5, more preferably be to being lower than in 1.48 scopes 1.35, and/or be the quantity that reduces inner spring to being lower than method for optimizing in 1.47 scopes 1.40, in comprising-inner spring, from employed spring assembly before the specific railcar, these assemblies have according to the AAR standard desired greater than 1.5 spring assembly reserve power.Special order of the spring that removes and quantity have no particular limits in order to obtain the reserve power of adjusting in spring assembly, and this area professional can be easy to determine these order and quantity by any given railcar type.

This specific arrangement with suitable disc spring diameter, spring bar diameter, spring material and spring height has been found that the reaction that operability can be provided, and this reaction helps to make bogie truck can satisfy the bogie truck performance specification M-976 that AAR formulates.

This structural arrangement of Figure 12 and Figure 15 is not unique utilizable spring structure or arrangement, but it has been realized the space constraint of bogie side frame window 18 and has considered the improvement of riding quality, increased the resistance sagging, and increased the vibration terminal speed of railcar suspension.The restriction that the operant response of any spring volume or characteristic all are counted as described wind spring material, is used to make described spring bar or the diameter of spring wire and the length and the height of spring of spring at its heat treatment.Therefore, there is any to be considered to imagine, promptly prepare by different structure and have the spring assembly that the spring of different-diameter varying number is formed, this spring assembly will be manipulable, thereby satisfy performance need with the constraint of satisfying described standard, but spring assembly has and is lower than 1.5 reserve power.

The additional detail of relevant exemplary modulation spring assembly can be 10/770,463 at application number, finds in the common unexamined patent of application on February 4th, 2004, and the disclosure content merges so that complete reference to be provided at this.

Another design of the factor of thinking to make bogie truck can meet new AAR bogie truck performance specification M-976 that works considers to be the use of the constant contact side bearing of long travel.One is preferably taken the design of control long travel side bearing is that application number at common pending trial is 10/808,535, and open in the common unexamined patent of application on March 25th, 2004, the disclosure content merges so that complete reference to be provided at this.Yet, can obtain at least 5/8 " and other long travel side bearing of stroke also can use.Such long travel side bearing can use the elasticity propulsion element to replace one or more disc springs.

First embodiment according to long travel side bearing of the present invention will be described with reference to figure 17-22.Side bearing assembly 300 has a main longitudinal axis that overlaps with the longitudinal axis of railcar.In other words, when described side bearing was installed on the railway bogie sleeper beam 16 (just partly showing in Figure 17), the spindle axis of described side bearing was perpendicular to the longitudinal axis of described sleeper beam.In other words, side bearing 300 meets axis 31 among Fig. 1 and sleeper beam 16 and meets axis 30 among Fig. 1.

Side bearing assembly 300 comprises as 310, one lids 320 of a base of major component, and one or more elasticity propulsion element 330, for example spring or elastic element.Shown in one exemplary embodiment in, three springs are provided, outer spring 330A, middle springs 330B and inner spring 330C are as propulsion element, each of these springs all has a different spring constant, so that total integrated load rate to be provided.

Base 310 is fixed on the sleeper beam 16 by suitable device.As shown in the figure, base 310 by fitting-up bolt 340 by bolt tightly on sleeper beam 16, packing ring 342 and assembling nut 344 are provided on the base flange 312 by assembly opening 346.As selection, base 310 can be by the rivet fix in position.Then, preferably, base 310 is soldered on the sleeper beam 16 along transverse side at least.

As best illustrated among Figure 18-19, sidewall 316 and antetheca and rear wall 318 that base 310 is relative.Each of antetheca and rear wall 318 comprises big a, opening of V-arrangement normally.Opening 314 allows during using described side bearing described spring 330A-C to be carried out visual inspection as viewing window.

In order to increase the trip distance of described side bearing, the bottom-to-top-height of wall 316,318 reduces 5/16 from original design ", such as at U.S. Patent number 3,748, use shown in 001 like that.This helps to make described spring obtain bigger stroke before lid 320 and base 310 cooperations and prevent farther stroke.In an one exemplary embodiment, base 310 has 3.312 " bottom-to-top-height of (+/-0.030), its wall 316,318 on flange 312, extend tap into 2.812 ".

With reference to figure 20-22, lid 320 is cup-shaped and comprises the sidewall 321 of downward extension, and the antetheca and the rear wall 322 that extend downwards, antetheca and rear wall in the sleeve mode round base 310.Antetheca and rear wall 322 provide big, a reverse groove 324 of V-arrangement normally, and groove is correspondingly in a certain position, and the groove 324 on this position base 310 helps to form observation windows.Sidewall 321 also comprises a groove 326.Lid 320 described downward wall extension 321,322 has hidden base 310 in such a way, though promptly at described spring 330 in its free height or under pressurized situation not, still between wall 321,322 and wall 316,318, provide a lot of coverings.This has eliminated with stop pin and has prevented the needs that the described relatively base of described lid is separated.

Lid 320 is further provided with one and goes up mating surfaces 328, following stop surfaces 323 and following recessed spring stayed surface 327.Preferably, all outward flanges 329 have all added top cover.This provides several purposes.It has reduced the weight of described lid.And, add upper top cover by giving described corner, produced the better mating surfaces that nestles up car body scuff panel (not shown, but in use be positioned at the below of car body, directly over the lid 320).Especially,, have been found that during use when described lid slides in the mode of friction engagement with described vehicle main body scuff panel and rotates, seldom have the scratch situation to take place by having the corner that adds top cover.Form better mating surfaces in order further to help, last mating surfaces 328 forms the plane in fact, preferably 0.010 " within the further wearing character of improving.

In order to help to provide the long travel of described spring, the length that lid 320 is shortened with base 310 taps into.In an one exemplary embodiment, lid 320 highly shortens 5/16 ", the design before having surpassed is with the stroke that allows lengthening spring 330 before lid 320 and base 310 cooperate and prevent further stroke.Lid 320 preferably has 3.50 " height, its sidewall 321 and 322 below lower support surface 327, extend downwards tap into 2.88 ".This allows described the lid before sidewall 321,322 collision flanges 312 deeper to hide on base 310.

Just as mentioned, side bearing lid 320 of the present invention and base 310 can use one or more propulsion elements, as spring 330 or elastic element (not shown).

In order to obtain at least 5/8 " long travel, preferably with the entity height of described spring from before the design employed height reduce.This is because the design of former spring is obtaining 5/8 " stroke before just become entity.That is to say that compression will be impossible so independent spring volume will compress further each other.

Here design and tested a lot of exemplary spring structures.Suitable exemplary type is provided in the form in Figure 23.These each can both in use have surpass 5/8 " stroke of (0.625 ").That is to say that each all has from load height (such as 4.44 ") to complete compression distance the stroke of (such as 3.68 "), when compression distance fully spring compressed fully or described lid and bottom seat cooperate surpassed 5/8 " stroke.A preferred spring assembly is #6.

Although three springs of each side bearing all are being described in a lot of embodiment, yet the spring that the present invention can use is not limited to spring in this table and spring still less, and even more spring.In fact, the quantity of side bearing and size can be special because of a special applications.Give an example, Light-duty Vehicle will be used softer spring rate and can use softer spring or use spring still less.And, have been found that the spring that has softer in fact spring constant than previously used spring by using, can obtain more performance.Have been found that this provides the slower reaction time to suspension system, and this has been found that the spring track and the curve that can be improved under the situation that does not have the reverse influence vibration.This also is found the sensivity reduction that can cause system height variation or component tolerances, therefore obtains more consistent preload in the bogie truck system.This easier balanced load and permission railcar keep more steady, have littler degree of dip or not only static the rolling but also dynamic rolling.

In order to obtain long fatigue life, the material that is used for base 310 and lid 320 changes over E level steel from C level steel, and the latter has bigger hardness and intensity.In order to help to obtain long fatigue life, on the outside face of base wall 316, provide the sclerosis worn-out surface.In addition, in order to prevent the too much wearing and tearing of moving and quickening, thereby by reduce the longitudinal clearance that reduces that previously used tolerance value provides between lid 320 and base 310.Give an example, this can obtain the strict more control to the casting of the sidewall of described lid 320 and base 310 and other forming process.Give an example, base 310 has 7.000 between the outside face of sidewall 316 " (+0.005/-0.015) fore-and-aft distance, and between the inside face of sidewall 322, have 7.031 " (+0.000/-0.020) fore-and-aft distance.This has caused one about 0.006 " to 0.024 " between controlled minimum/maximum space gap, this is than previously used tolerance more closely and littler gap, and causes control that described bogie truck has been improved in fact.When base side wall 316 is in maximum allowance 7.005 " and described lid sidewall be in minimal tolerance 7.011 " time just obtained minimum clearance.When base side wall 316 is in minimal tolerance 6.985 " and described lid sidewall be in maximum allowance 7.031 " time just obtained maximum clearance.And, keep between upper surface 327 and the lower surface 323 1.25 " distance of (+/-0.030) also is very important, like this can assurance at least 5/8 before lid 320 is fully compressed on the base 310 " stroke.

Because the possibility of different spring assemblies, also expectation provides the feature of a safety, and this feature can prevent the interchangeability of improper element for given application.In order to realize this point, one exemplary embodiment is not only to covering 320 but also all provide the wedging structure to prevent the mispairing of element to base 310.And, can provide spring lock structure to covering 320, this spring lock structure has prevented the inappropriate combination of the spring that is used.

Having used first one exemplary embodiment of all three spring 130A, 130B, 130C to look back in Figure 17 is demonstrated out.This application will be used to the heavy railway car and can use any three spring assemblies cited among Figure 23.Yet preferred spring assembly is the #6 among Figure 23.The use of three spring assemblies is particularly suitable for surpassing 65,000 pounds railcar, typically between 65,000 pounds to 110,000 pounds.Such a railcar often is boxcar, all steel coal car, multilayer car stand compartment and at the similar car body that has 286,000 pounds of gross weights aspect the rail grade.

This structure comprises one the first wedging structure that is made of vertical semicircle wedging structure 350, and this vertical semicircle wedging structure 350 is provided at (seeing Figure 18) on the outer corners on the relative diagonal line of base 310 and corresponding vertical semi-circular projection wedging structure 360 (seeing Figure 20) and is provided at and cover on 320 the corresponding interior corner.By these wedging structures, the base and the lid that only are used for this application will be allowed to cooperate and imbrication.This has prevented the mispairing of element.And described wedging structure 350,360 preferably can prevent the improper location of element.Give an example, described wedging structure preferably should prevent a suitable but use of having rotated 180 ° lid from correct direction.Different wedging structures can offer other application, as medium-sized light railway car or Light-duty Vehicle.Additional detail as the embodiment that selects can be 10/808,535, find in the common unexamined patent of application on March 25th, 2004 at application number.

The use of above-mentioned wedging structure 350,360 has obtained the proper fit of base and cap member.Yet the structure that also needs to add is used to special application to guarantee suitable spring assembly.Embodiment among Figure 17 has used all three springs.Because this point no longer needs spring lock structure.Similarly, the downside of the lid 320 of this embodiment will be as presenting among Figure 22.Yet, in other embodiments, can use the various combination of spring 330A-330C.In order to prevent the use of spring 330C, the following recessed spring stayed surface 327 of the lid 320 among Figure 24 provides a suitable spring lock structure 370, and it has prevented the insertion of improper spring.In this case, spring lock structure 370 can be a boss that protrudes downwards, and its size can prevent the use of little spring 330C, but its not overslaugh of size spring 330A or 330B are leaning on and cover 320 in-to-in spring stayed surfaces, 327 layouts.Similar, in order to prevent the use of middle springs 330B, the following recessed spring stayed surface 327 of lid 320 can provide one second exemplary spring lock structure 370, as shown in figure 25, this spring lock structure protrudes and has prevented the use of middle springs 330B downwards under the situation of the layout that does not have overslaugh spring 330A or 330C.Other structure of spring lock structure all is considered.Give an example, if only outer spring 330A is used in expectation, one the 3rd exemplary spring lock structure 370 so as shown in figure 26 just can provide to prevent the use of inner spring and middle springs 330B, 330C.Therefore, the combination of base and lid wedging structure 350,360 and described spring lock structure 370 have prevented to be used for the exchange of the improper element of a special applications.

Thereby by in side bearing of the present invention, using special spring constant to obtain additional advantage.Three springs design in the past has high spring constant, and this high spring constant is considered to obtain suitable load support and gives the railcar damping necessary.Give an example, for 65,000 pounds railcar, a lot of designs in the past have about 7100 pounds/inch integrated load rate (3705 pounds/inch of outer springs, 2134 pounds/inch of middle springs, 1261 pounds/inch of inner springs).Example on Figure 23 has fallen into this kind.Yet, have been found that load factor by the described spring of remarkable minimizing, in fact make them become softer, what can obtain to improve in fact takes and the load balance characteristic.If described integrated load rate so just can obtain a lot of benefits between about 4,000 to 6,000 pounds/inch.If this ratio far below 4,000 pounds/inch, might will disengage with the bottom surface of described vehicle main body by side bearing, this is undesirable.Along with load factor towards 6,000 pounds of/inch increases, just can obtain similar benefit.Yet, being higher than this scope, described spring is just to production tolerance and structural deviation sensitivity.

The bottom of Figure 23 (example #6) has showed that according to a preferred embodiment of the present invention this embodiment has used about 4506 pounds/inch total integrated load rate (2483 pounds/inch of outer springs, 1525 pounds/inch of middle springs, 498 pounds/inch of inner springs).A near spring assembly the lowest limit of 4,000 to 6,000 pounds/inch of described preferable range.At first, it allows described side bearing to change for system height and the tolerance sensivity reduction that becomes.In other words, the little deviation from a side bearing on the bogie truck to another side bearing has been found that actual preload is had slight influence.Therefore, the spring with this preload scope has been found that to have more consistent preload from the side bearing to the side bearing, even have small construction height or other tolerance variation or have the disunity of bearing.This makes load balance easily and allows the railcar held stationary, has littler degree of dip or not only static the rolling but also dynamic rolling.The second, low like this load factor provides the slower reaction time for suspension system, and this has been found that the spring track and the curve that can be improved under the situation that does not have the reverse influence vibration.Yet, just as mentioned, can use the spring trip rate of the increase that taps into 6,000 pounds/inch.Yet in order to obtain similar performance, different design tolerances must strictly be controlled because along with described spring rate towards 6,000 pounds of/inch increases, the sensivity of structure and tolerance variation is also being increased.Therefore, if the not control suitable to these tolerances, such a deviation will cause uneven load, if caused a side bearing on the bogie truck structurally different with other bearing, described vehicle main body can become the state that undesirable leaning angle is arranged from the state on a plane.

Huge less before the combination of this structure has also obtained relatively on the design-calculated weight.Give an example, exemplary side bearing 100 has been found that to have only 47.3 pounds weight, and this had reduced for 55.9 pounds than former design-calculated.

Another design of the factor that works that is considered to make bogie truck meet new AAR bogie truck performance specification M-976 considers it is the use of elastic support pad.In US Patent 6,371, Smith discloses a kind of suitable elastic support pad in 033, and the disclosure content merges so that complete reference to be provided at this.

Later with reference to figure 1, each representative type bogie truck 10 comprises a pair of bogie side frame 12,14 that is supported on the wheel set 20,22.Hollow sleeper beam 16 extends between the spring assembly 36 that is installed on the described bogie side frame and is supported on the spring assembly.Bogie side frame 12,14 comprises a top member 400, compression element 410, take up member 420, post 430, bearing 440, bearing top 450, bearing 460 and bearing adapter 470.Each end of sleeper beam 16 comprises that one protrudes the wing, is called gib 480.Each end of bogie side frame 12,14 provides a bearing 440, and the size design of bearing gets and can mesh respectively with bearing assembly 460, and can comprise an opening, this opening and bearing adapter 470 engagements.In the design before great majority, described bearing adapter 470 pushes up 450 direct contacts with bearing and scrapes the bearing top.Yet have been found that, a resilient elastic body that just uses in limited application props up that seat cushion 490 has reduced rail power and works with other bogie structure of the present invention and improves the motion control of bogie truck before this, and help to obtain to meet the bogie truck design of M-976 standard, this seat cushion is between described bearing top 450 and described bearing adapter 470.

A preferred seat cushion is guest's sunset additional adapter system (Pennsy AdapterPlussyetem).This pad between described bogie side frame and described adapter mutual action to improve curve performance.Described guest's sunset additional adapter can be buied from Pennsylvanian west chester guest sunset company (Pennsy Corporation of West Chester).The another kind of type of propping up seat cushion is the cushion of being produced by Lord Corporation (Lord Corporation), and it is made by natural rubber.It is fatigue durability and vertical stiffness very big.Similarly, it can support the load of described railcar.Yet it is worked under friction stress, so it makes described bogie truck assembly operating track become straight when turning or curvilinear motion, has withdrawed from curvilinear path.By reducing wheel for rail power, wear condition has been enhanced, and drives control and also is improved.Therefore, curve performance has greatly been improved, and has reduced the wearing and tearing of bogie truck element simultaneously.

Similarly, the invention provides a combination of a plurality of project organizations, this combination cooperates in harmony with the motion control that is improved, and the motion control that improves has improved riding quality, increased the resistance sagging, strengthened the vibration terminal speed of railcar, improved squareness suspension, improved curve performance, and improved wearing character so met or surpass the bogie truck performance specification M-976 that nearest AAR formulates.This combination of a plurality of structures comprises two or more following structures: " adjustment " spring assembly, the constant contact side bearing of long travel, " wide " friction shoe or other friction shoe with squareness of increase, and/or an elastic support pad.

When unique specific embodiments of the present invention was described and shows, clearly, different selections and modification can be made with this.Those skilled in the art also will recognize in these illustrative embodiment can add some etcetera.Therefore, the purpose of Fu Jia claim is to cover all these selections, modification and the etcetera that can fall in the true scope of the present invention.

Claims (22)

1. railcar bogie truck is used to have the railcar of at least 286,000 pound specified rail total weight, comprising:

Two bogie side frames, each bogie side frame has a bearing that is formed at its opposed end and defines the roughly vertical post that is positioned at a middle bogie side frame opening of described bearing, be provided at the friction surface on the described vertical post, each bearing has a base openings, and its size can receive a bearing adapter;

A sleeper beam, it is provided with sidewards with respect to described bogie side frame and is supported in described bogie side frame open interior, and described sleeper beam is included in the side shaft rim on the upper surface of the described sleeper beam between the described bogie side frame;

And following at least two:

The long travel side bearing, be arranged on each side shaft rim, described long travel side bearing comprises a base, a lid and at least one elasticity propulsion element, described elasticity propulsion element by before the compression fully or before described base and lid reduced as far as possible, this elasticity propulsion element had at least 5/8 " stroke;

One truck suspension, it is made of a spring assembly that is provided in each bogie side frame opening, has supported described sleeper beam respective end portions, and described spring assembly has the minimum reserve power less than 1.5;

The friction shoe of high verticality is arranged between described sleeper beam and the described bogie side frame opening, and each friction shoe comprises a vertical substantially wall and a friction face, and described vertical wall can mesh with friction surface; And

One cushion, it is arranged on the top of described carrier openings, therefore in use can be arranged between described support and the described bearing adapter.

2. railcar bogie truck as claimed in claim 1, wherein said friction shoe have effective friction face of one about at least 8 inches.

3. railcar bogie truck as claimed in claim 2, wherein said friction shoe are to have two split wedge designs that separate watt parts and an insertion parts, and described two separation watt parts are advanced outwards to launch during obtaining effective friction face at sleeper beam.

4. railcar bogie truck as claimed in claim 2, wherein said friction shoe are compound oblique angles watt.

5. railcar bogie truck as claimed in claim 2, wherein said friction shoe are the droop types.

6. railcar bogie truck as claimed in claim 2, wherein said friction shoe are the variable deviation types.

7. railcar bogie truck as claimed in claim 1, wherein said bogie truck comprise the long travel side bearing at least, have less than a truck suspension of 1.5 reserve power and the high verticality friction shoe with effective friction face of at least 8 inches.

8. railcar bogie truck as claimed in claim 1, wherein said bogie truck comprises the long travel side bearing at least, have less than a truck suspension of 1.5 reserve power and be arranged on the top of described carrier openings, therefore in use can be arranged on a cushion between described support and the described bearing adapter.

9. railcar bogie truck as claimed in claim 8, wherein said cushion is made by natural rubber or plastics.

10. railcar bogie truck as claimed in claim 1, wherein said long travel side bearing have the combination load rate between about 4,000 to 6,000 pounds/inch.

11. railcar bogie truck as claimed in claim 10, wherein said long travel side bearing have a longitudinal space slit between described base and described lid, this slit is between about 0.006 to 0.046 inch.

12. railcar bogie truck as claimed in claim 1, wherein said long travel side bearing have an elasticity propulsion element that exists with at least one wind spring form.

13. a railcar bogie truck is used to have the railcar of at least 286,000 pound specified rail total weight, comprising:

Two bogie side frames, each bogie side frame has a bearing that is formed at its opposed end and the roughly vertical post that defines a bogie side frame opening between described bearing, be provided at the friction surface on the described vertical post, each bearing has a base openings, and its size can receive a bearing adapter;

A sleeper beam, it is provided with sidewards with respect to described bogie side frame and supports in described bogie side frame open interior, and described sleeper beam is included in the side shaft rim on the upper surface of the described sleeper beam between the described bogie side frame;

The long travel side bearing, be arranged on each side shaft rim, described long travel side bearing comprises a base, a lid and at least one elasticity propulsion element, described elasticity propulsion element by before the compression fully or before described base and lid reduced as far as possible, this elasticity propulsion element had at least 5/8 " stroke;

One truck suspension, it is made of a spring assembly that is provided in each bogie side frame opening, has supported corresponding described sleeper beam end, and described spring assembly has the minimum reserve power less than 1.5;

The friction shoe of high verticality, it is arranged between described sleeper beam and the described bogie side frame opening, and each friction shoe comprises a vertical substantially wall and a friction face, and described vertical wall can mesh with friction surface, wherein, described friction shoe is kept the basic squareness of described sleeper beam and described bogie side frame; And

One cushion, it is arranged on the top of described carrier openings, therefore in use can be arranged between described support and the described bearing adapter.

14. railcar bogie truck as claimed in claim 13, wherein said friction shoe have effective friction face of one about at least 8 inches.

15. railcar bogie truck as claimed in claim 14, wherein said friction shoe are to have two split wedge designs that separate watt parts and an insertion parts, described two separation watt parts are advanced outwards to launch during obtaining effective friction face at sleeper beam.

16. railcar bogie truck as claimed in claim 13, wherein said friction shoe are compound oblique angles watt.

17. railcar bogie truck as claimed in claim 13, wherein said long travel side bearing have an elasticity propulsion element that exists with at least one wind spring form.

18. railcar bogie truck as claimed in claim 13, wherein said cushion is made by natural rubber or plastics.

19. railcar bogie truck as claimed in claim 13, wherein said long travel side bearing have the combination load rate between about 4,000 to 6,000 pounds/inch.

20. railcar bogie truck as claimed in claim 19, wherein said long travel side bearing have a longitudinal space slit between described base and described lid, this slit is between about 0.006 to 0.046 inch.

21. railcar bogie truck as claimed in claim 14, wherein said friction shoe are the droop types.

22. railcar bogie truck as claimed in claim 2, wherein said friction shoe are the variable deviation types.

Images